Control system for the drive of detaching rollers in textile combing machines

ABSTRACT

AN ECCENTRIC IS FREELY MOUNTED ON THE COMB DRIVE SHAFT TO IMPART A RECIPROCATING MOVEMENT TO ONE OF THE INPUT SHAFTS OF THE DIFFERENTIAL GEAR WHILE THE OTHER INPUT SHAFT IS UNIFORMLY DRIVEN FROM THE DRIVE SHAFT. THE DETACHING ROLLERS OF THE COMBING MACHINE ARE THUS RECIPROCATED IN A PILGRIM STEP MANNER.

June 15, 1971 ElCHENBERGER ETAL 3,584,346

CONTROL SYSTEM FDR THE DRIVE OF DETACHING ROLLERS IN TEXTILE COMBING MACHINES Filed Sept. 23, 1968 INVE NT 0R5 HANS UL PIC H E/CHEA/B W54 PETER \SCHWENGEL ER United States Patent US. Cl. 19232 Claims ABSTRACT OF THE DISCLOSURE An eccentric is freely mounted on the comb drive shaft to impart a reciprocating movement to one of the input shafts of the differential gear while the other input shaft is uniformly driven from the drive shaft. The detaching rollers of the combing machine are thus reciprocated in a pilgrim step manner.

This invention relates to a control system for the drive of the detaching rollers in textile combing machines.

In the combing of fibers in many combing machines, a layer of fibers extending from a nipper assembly is combed out and pushed by the nipper as the nipper swings forwardly on opening to a detaching unit consisting of detaching rollers which convey the fibrous material forward to the next processing station.

In combining machines that operate in accordance with the Heilmann system, the detaching rollers follow a socalled pilgrim-step movement, that is, the detaching rollers rotate two steps forwardly and one step backwardly. In rotating forwardly, these detaching rollers remove the layer of fibers which have been combed by a circular comb and extend from the nipper and advance the combed layer forwardly. On rotating backwardly, in timed sequence with a second combing cycle, the detaching rollers at first return part of the web removed in the first combing cycle so that the ends of the returned web are placed on the ends of the fibers from the following combed tuft. The detaching rollers then reverse again and rotate forwardly to remove the second layer of fibers from the open nippers. This last movement corresponds to the detaching movement of the detaching rollers. The newly detached web thus is overlapped on the returned web and the two webs become combined with one another under the pressure of the detaching rollers and the adhesion between the fibers of the webs. Thus, the detaching rollers not only change direction twice during each combing cycle but also travel a shorter distance during return movement than during forward movement.

In combing machines that operate in accordance with the Nasmith system, the detaching rollers while following the pilgrim-step movement remain stationary after detachment for a while until the next combing cycle.

The pilgrim step movement of the detaching rollers of these above combing machines has given rise to many different control systems for controlling the drive of the detaching rollers. For example, in Nasmith-type combing machines, this complicated movement is initiated by two oscillating toothed segments in conjunction with gear clutches. In other known types of drive systems for the 3,584,346 Patented June 15, 1971 detaching rollers of combing machines, the movement of the detaching rollers is controlled by way of a cam disc. It is also known that cams or cam grooves can be used to produce a reciprocatory movement. Furthermore, attempts were made to impart the pilgrim-step movement to the detaching rollers through a crank-drive, consisting of a crank and crank-rod driven from a circular-comb shaft through the intermediary of the planetary wheels of a differential drive, which movement is then added to a uniform rotary motion imparted to the differential drive from the comb drum shaft and transmitted to the detaching rollers. This arrangement results in eliminating the standstill time of the detaching rollers. However, this is disadvantageous since the standstill time is necessary in order to feed back the fibers through the detaching rollers when the combing operation of the circular comb is ended. The known drive arrangement for the detaching rollers, which as in Ger. Pat. 1,133,288 dated July 12, 1962 consists of a controllable differential drive, of a knee-lever as a controlling or driving element for the differential drive, and of a crank-drive as an operating means for the knee-lever, in comparison with the previously known knee-lever drives, merely increases the standstill time of the detaching rollers, through the buckling of the knee-lever, by a small amount beyond the stretchedout position of the knee-lever. In other known combing machines, the movement of the detaching rollers is controlled through eccentrics and cam drives.

These drive arrangements, however, have the drawback that the to and frow movements merge into one another and through this there likewise exists no standstill between the two movements.

Although the control of the drive of the detaching rollers through a cam disc is a relatively simple solution because the movement itself is variable within a wide range by appropriately displacing the cam, cam control is only suitable for combing speeds of up to approximately 200 combing cycles per minute. It is not possible to further substantially increase the combing cycles with cam discs because, if this were the case, the degree of wear on the cam track or guide roller would be excessive.

Accordingly, it is an object of the present invention to provide a control system enabling combing to be carried out at speeds of greater than 200 combing cycles per minute.

It is another object of the invention to provide a control system for the detaching rollers of a combing machine which operate without any disc cams.

It is another object to have the control system remain stationary for more than of one combing cycle in order at this stage to achieve a fast forward movement and a somewhat slower return movement.

Briefly, the invention provides a control system for the drive of detaching rollers in a combing machine in which an input shaft of a differential gear receives a uniform drive while another input shaft reecives a fast forward movement and a somewhat slower return movement with a stationary phase, so that an output shaft of the differential gear transmits the superimposed movements to the detaching rollers. The forward and backward movement or reciprocation as well as the stationary phase imparted to the second input shaft can be produced very easily by means of an eccentric which is mounted for free rotation on the frame and which receives a non-uniform rotating movement by way of a pull rod fron a crank driven at a constant speed of rotation which is mounted offset relative to the center of rotation of the eccentric. The eccentric is intended to carry a rocker which is pivotally supported by means of a supporting lever rotatably mounted on the frame and which transmits the movement imparted to it from the eccentric through a coupling such as a link to a control lever for the second input shaft of the differential gear.

By virtue of the control system in which a differential gear superimposes a uniform drive and a reciprocating movement generated by the control system and transmits the superimposed movements to the detaching rollers, it is possible on account of the travelling movements of the point at which the coupling is articulated to the rocker not only to vary the additional rotating movement to be superimposed upon one of the sun wheels of the differential gear, i.e. the speed at which and/or the direction in which the shaft of the differential gear rotates but also, in particular, to alter the time for a sequence of successive working stages which occur at pre-set intervals and which together make up the necessary rundown of the rotating movement of the detaching rollers. In addition, a much larger number of combing cycles is obtained by using a non-uniformly driven eccentric in the system for controlling the drive of the detaching rollers.

These and other objects and advantages of the invention will become more apparent from the following detailed description and appended claims taken in conjunction with the accompanying drawings in which:

FIG. 1 illustrates a partially broken elevational view of a control system according to the invention with a non uniformly driven eccentric and a differential gear;

FIG. 2 illustrates a view taken on line II-II of FIG. 1;

FIG. 3 diagrammatically illustrates the control system with the non-uniformly driven eccentric;

FIG. 4 illustrates a view taken on line IVIV of FIG. 1 of an adjusting disc in which a pull-rod is slidably mounted in a slot; and

FIG. 5 illustrates an adjusting disc in which a pin of a gear wheel is mounted in a slot.

Referring to FIG. 1, a circular comb shaft 1 which rotates a circular comb as is known is mounted in .a machine frame 7 of a combing machine and is driven by a drive shaft 25 by way of a gear-wheel 26 mounted on the drive shaft 25 and a gearwheel 3 mounted on the circular comb shaft 1. The drive shaft 25 receives its drive from a motor (not shown) via a pulley wheel 24. Further, an adjusting disc 4 is mounted on the circular comb shaft 1 and is connected with the gearwheel 3 through an adjusting screw *6.

Referring to FIGS. 1 and 2, a pull rod 10 is pivotally connected to the adjusting disc 4 at point E by means of a crank pin 5. Alternatively, the pull rod 10 can be pivotally connected to the gearwheel 3 without the intermediary of the adjusting disc 4. The pull rod 10 further engages an eccentric 8 freely mounted on the frame 7 at point D through a pin 9. When a movement is imparted to the eccentric 8 from the circular comb shaft 1 through the adjusting disc 4 and the pull rod 10, this movement is transmitted by the eccentric 8 to a rocker 11 mounted concentrically of the eccentric 8. The rocker 11 is pivotally connected on the periphery by means of a pin 15 at point I to a supporting lever 14 which is rotatably mounted on a nipper drive spindle 22, while at the opposite point of its periphery, the rocker 11 is pivotally connected through a pin 12 to a link 16 at point G. The link 16 is in turn pivotally connected through a pin 19 to a control lever 17 at point P. The control lever 17 is fixed to a shaft 20 of a differential gear 21.

As shown in FIG. 1, a link of the differential gear 21 receives a rotating movement in one end in the same direction and at a uniform speed from a gearwheel 27 mounted on the circular comb shaft 1 by way of an intermediate gear 28 mounted on a pin 29 fixed to the machine frame 7, and a link wheel 30 on the periphery of the link 30. This rotational movement is imparted to a planet gear 32 in the differential gear 21 which is connected to the link 30' and which rolls around a sun gear 31 fixed on the shaft 20 of the differential gear. The planet gear 32 is further connected with another planet gear 32 to impart rotary motion thereto. This planet gear 32 meshes with and drives a sun gear 33 which is rotatably mounted on the shaft 20 of the differential gear and connected to a gearwheel 34. The gearwheel 34 drives the detaching roller 23 through gearwheels 35, 36 and 37 mounted outside the differential gear 21.

When the eccentric 8 moves, the rocker 11 makes eccentric movements which are transmitted through the link 16 at point G to the control lever 17 at point F and hence to the shaft 20 of the differential gear 21. The eccentric movement is then superimposed on the rotating movement generated from the circular comb shaft 1 via gear 28 and link 30 in one and the same direction and at a constant speed and transmitted from the differential gear 21 to the detaching rollers 23.

Referring to FIG. 3, the point I at which the supporting lever 14 is pivoted, the pivot point G and the center C of the rocker 11 are initially situated on a straight connecting line V Since the rocker 11 is pivotal at point I about a point K at which the supporting lever 14 is pivotally connected to the nipper drive spindle 22, the center C of the rocker 11 follows a circular path K with its center at point B when the eccentric 8 moves. As a result, point G moves along an ellipse-like path K By virtue of the link 16, the movements of point G along the ellipse-like path E produce reciprocating arcuate movements along a circular curve K for the point P, with the result that point P and hence the control lever 17 oscillate about a point H. The ellipse-like path E may therefore be regarded as a coupling curve.

As shown in FIG. 3, the centers A of the circular comb shaft 1 and B of the eccentric 8 do not coincide but are offset from each other. Thus, when the pull rod 10 rotates, the point E rotates along a circular path E about the center A of the shaft 1, while the point D rotates on a circular path K about the center B of the eccentric 8. The eccentric 8 is therefor non-uniformly driven. Owing to the supporting lever 14, these rotating movements generate for the center C of the rocker 11 a movement along a circular path K with a center at B, the center of rotation of the eccentric 8, and for point G movement along the ellipse-like path E so that pivot G completes one' revolution from G through G" and G'" back to G. For example, with the center C of the rocker at C, point I of the supporting lever at J and point G at G (as shown in chain lines), the positions of the points D and E correspond to points D and E. The zone G to G through which point G travels on the ellipse-like path E thus produces a fast return movement of the detaching rollers 23 (return) through the movements of point F and the control lever 17; the zone from G" to G'", a forward movement of the detaching rollers 23 (detachment of the fibers); and the zone 6 to G a prolonged standstill time or stoppage of the detaching rollers 23.

A movement of point F on the circular curve K from F to F corresponds to a movement of point G on the ellipse-like path E from G to G", as a result of which the control lever 17 completes a fast movement, in consequence of which the detaching rollers 23 complete a backward movement which continues up to G" in path E Due to the continuing movement of point G from G" towards 6, point F again moves from position F" on the circular path K towards F. At the same time, the control lever 17 rotates back in the opposite direction and in doing so imparts a forward movement to the detaching rollers 23 continuing until point G reaches position G on the ellipse-like path E and hence until point F has reached position F on the circular path K When point G travels along the ellipse-like path E between G" and G, point P stays in position at P which in practice corresponds to stoppage of the control lever 17 and hence of the shaft 20 of the differential gear and also of the detaching rollers 23 in relation to the additional superimposed reciprocating movement imparted to the differential gear 21 and hence to the detaching rollers 23. If point F is to stay in position F, point G must move along an approximately circular path around point F in the section G"-G of the ellipse-like path E As shown in FIG. 3, the section G"G of the ellipse-like path E corresponds to a circular path with its center at point P. When point B moves along the circular path K about the center A of the shaft 1 by more than 180, the point D of the pull rod 10 will turn through less than 180 on the circular path K owing to the non-uniformly driven eccentric 8, while point G will travel along a circular path covering less than 180 in that section of the ellipse-like path E stretching from G to G, as a result of which the control lever 17 will come to a standstill for more than 180 of one combing cycle. In the drive system according to the invention, the dwell time of point F is extended by the non-uniform drive of eccentric 8 to more than 180 of one combing cycle, which would not be achieved by an ordinary crank drive in which the center of the circular comb shaft coincides with the center of the eccentric 8.

The movement path of the point G produced by the revolving eccentric 8 through the center point C of the rocker 11 oscillating on the circular path K thus produces the reciprocating movement of pivot F on the circular path K between the positions F and F which are transmitted through the control lever 17 and the shaft 20 of the differential gear to the differential gear 21 and then to the detaching rollers 23 as a result of which the rollers 23 make a fast backward movement followed by a forward movement, coming to a standstill during the dwell time of point P in position F corresponding to the distance travelled by point G on the elliptical path E between points G and G. Adjustment of the particular moment at which the backward movement, forward movement and stoppage of the detaching rollers 23 are initiated, is effected by means of the adjusting screw 6 on the adjusting disc 4 by which points G, G and G may be displaced as required and fixed.

The invention can undergo further alterations. Thus it is also possible to influence the pilgrim-step movement in that the point of aritculation E on the adjusting disk 4 is angularly adjustable relatively to the drive gearwheel 3 for the circular shaft 1, as is further shown in FIGS. 4 and 5. According to FIG. 4, an adjusting disk 39, disposed on a circular-comb shaft 38, is connected by a screw 40 with a gearwheel (not shown) also disposed on the circular-comb shaft back of the plane of the drawing. The

adjusting disk 39 has a slot 41 which runs circumferentially and in which is disposed a pin 42, upon which is povotably fastened a pull-rod (not shown) situated in front of the plane of the drawing. The pin 42 is further fastened to the adjusting disk 39 by means of a nut 43. By loosening the nut 43 and shifting the pin 42 in the slot 41, the point of articulation M of the pull-rod to the adjusting disk 39 can be set into another desired angle relatively to the gearwheel.

According to FIG. 5, an adjusting disk 45 is disposed on a circular-comb shaft 44 and has a pin 46 upon which is pivotably disposed a pull-rod (not shown) situated in front of the plane of the drawing. The adjusting disk has a slot which runs circumferentially and in which is disposed a pin 48 of a gearwheel (not shown) situated back of the plane of the drawing. By means of a nut 49, the adjusting disk 45 is fastenend to the pin 48. By loosening the nut 49 and shifting the slot 74 on the pin 48 an articulaiton point N of the pull-rod via pin 46 on the adjusting disk 45 can be set to a desired angle relatively to the gearwheel.

With the forms of construction of FIGS. 4 and for the adjusting disks 39 and 45 respectively, and the standstill time of the detaching rollers can be adjusted as desired.

Further, it is noted that the pull rod 10 can be mounted at one end to a crank which is not connected to the gear wheel 3 or the drive shaft of the circular comb 1 of a combing machine. Also, the adjusting disc 4 can be mounted on another drive shaft mounted separately from the drive shaft of the circular comb.

The invention thus provides a control system for the detaching rollers of a combing machine wherein the pilgrim step movement of the detaching rollers, that is, a greater forward movement than backward movement, is achieved in a simple efficient manner.

What is claimed is:

1. A control system for the drive of a plurality of detaching rollers in a rectilinear combing machine having a frame, a differential gear connected to said detaching rollers, and a drive means connected to said differential gear for imparting a uniform rotary movement thereto; said control system comprising an adjusting disc rotatably mounted in said frame,

an eccentric mounted in offset relation to the center of rotation of said adjusting disc,

a pull-rod pivotably mounted at each end thereof to said adjusting disc and said eccentric respectively to impart a non-uniform rotary motion of constant speed to said eccentric during rotation of said adjusting disc,

a rocker supported on said eccentric for movement thereby,

a supporting lever rotatably mounted in the combing machine and pivotably connected to said rocker at a peripheral point,

a control lever connected to said differential gear to impose a motion thereon, and

a coupling connected to said rocker and said control lever for transmitting the movement imposed on said rocker from said eccentric to said control lever and said differential gear whereby a supplementary rotary movement is superimposed on said uniform rotary movement of said differential gear.

2. A control system as set forth in claim 1 further comprising a gearwheel connected between said drive means and said differential gear for transmitting movement therebetween, and a sun-wheel in said differential gear con' nected to said control lever for transmitting movement therebetween.

3. A control system as set forth in claim 1 further comprising a circular comb shaft in said drive means, said adjusting disc being mounted on said circular comb shaft.

4. A control system as set forth in claim 3 wherein said adjusting disc is angularly adjustable with respect to said circular comb shaft.

5. A control system as set forth in claim 1 wherein said supporting lever is rotatably mounted on a nipper drive spindle in the combing machine.

6. A control system as set forth in claim 1 wherein said coupling is connected to said rocker at a point opposite the point of connection of said supporting lever to said rocker.

7. A control system as set forth in claim 6 wherein said points are diametrically disposed on said rocker.

8. A control system as set forth in claim 1 wherein said coupling is connected at a first point to said control lever and at a second point to said rocker, said first point moving in a pivotal reciprocating path in response to said second point moving through an ellipse-like path including a circular portion with said control lever having a prolonged standstill time.

9. A control system as set forth in claim 1 wherein said coupling is a link.

10. A control system for the drive of a plurality of detaching rollers in a rectilinear combing machine comprising a differential gear having a first input shaft for receiving a reciprocating movement, a second input shaft 7 for receiving a uniform movement, means for superimposing said movements therein, means for imparting said superimposed movements to the detaching rollers, a rotatable gear wheel, an eccentric mounted in oifset relation to the center of rotation of said gear Wheel, a pull rod pivotally mounted at each end thereof to said gear wheel and said eccentric respectively to rotate said eccentric with a non-uniform rotatory movement during uniform rotation of said gear wheel, a rocker supported on said eccentric for movement thereby, a rotatably mounted supporting lever pivotably connected to said rocker, a link pivotably connected to said rocker, and a control lever secured on said first input shaft and pivotably connected to said link whereby movement of said rocker is imparted through said link and said control lever to said first input shaft to reciprocate said control lever and said first input shaft.

References Cited UNITED STATES PATENTS 1,169,046 1/1916 Lunn 19232 1,464,098 8/1923 Helland 19232 3,232,132 2/1966 Kawamura et a1. 19-231X FOREIGN PATENTS 822,291 10/1959 Great Britain 19293 583,573 10/1958 Italy l9225 DORSEY NEWTON, Primary Examiner 

